CN109219693B - Rotary machine - Google Patents

Rotary machine Download PDF

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Publication number
CN109219693B
CN109219693B CN201680084109.5A CN201680084109A CN109219693B CN 109219693 B CN109219693 B CN 109219693B CN 201680084109 A CN201680084109 A CN 201680084109A CN 109219693 B CN109219693 B CN 109219693B
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CN
China
Prior art keywords
housing
impeller
bearing
fastening member
abutting
Prior art date
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Active
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CN201680084109.5A
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Chinese (zh)
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CN109219693A (en
Inventor
永代行日出
竹下友祥
段本洋辅
小川真司
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Mitsubishi Heavy Industries Engine and Turbocharger Ltd
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Mitsubishi Heavy Industries Engine and Turbocharger Ltd
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Publication of CN109219693A publication Critical patent/CN109219693A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/162—Bearing supports
    • F01D25/164—Flexible supports; Vibration damping means associated with the bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • F01D25/243—Flange connections; Bolting arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/04—Antivibration arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
    • F02B33/40—Engines with pumps other than of reciprocating-piston type with rotary pumps of non-positive-displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/39—Retaining components in desired mutual position by a V-shaped ring to join the flanges of two cylindrical sections, e.g. casing sections of a turbocharger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/96—Preventing, counteracting or reducing vibration or noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/22—Pumps

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Supercharger (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

A rotary machine is provided with: a rotating shaft; an impeller attached to the rotating shaft; an impeller housing that houses the impeller; a bearing housing that houses a bearing that rotatably supports the rotating shaft and is fastened to the impeller housing; and a fastening member that fastens the impeller housing and the bearing housing in an axial direction of the rotary shaft, wherein the impeller housing, the bearing housing, and the fastening member each have an abutting surface that abuts against each other in a direction intersecting the axial direction of the rotary shaft, and a thin plate member that is separate from the impeller housing, the bearing housing, and the fastening member is provided at least one portion between the abutting surfaces.

Description

Rotary machine
Technical Field
The present disclosure relates to rotary machines.
Background
As a rotary machine, for example, a turbocharger or the like is known which is mounted on an automobile or the like and increases an intake air amount to increase an output.
In a rotary machine such as a turbocharger, vibration of a rotary shaft due to imbalance in the weight of the rotary shaft or the like propagates to a housing, and the shaft vibration becomes an excitation force to vibrate the housing, which causes a problem of noise generation.
In patent document 1, in order to suppress such vibration, a vibration suppressing material having damping properties or elasticity is provided on the outer side of a bearing bush that supports a rotating shaft, and an inertial mass body that vibrates in a phase opposite to that of the bearing bush when the bearing bush vibrates is provided.
Documents of the prior art
Patent document
Patent document 1: japanese unexamined patent application publication No. 2010-174811
Disclosure of Invention
Problems to be solved by the invention
The vibration-proof scheme disclosed in patent document 1 requires the provision of a vibration suppressing material and an inertial mass body, and has a problem of increased weight and complicated structure.
In view of the above problems, an object of at least one embodiment of the present invention is to suppress vibration and noise generated in a rotary machine with a simple configuration.
Means for solving the problems
(1) Some embodiments provide a rotary machine, comprising:
a rotating shaft;
an impeller attached to the rotating shaft;
an impeller housing that houses the impeller;
a bearing housing that houses a bearing that rotatably supports the rotating shaft and is fastened to the impeller housing;
a fastening member that fastens the impeller housing and the bearing housing in an axial direction of the rotary shaft,
the impeller case has an impeller case side abutting surface extending in a direction intersecting an axial direction of the rotary shaft at a fastening portion to which a fastening force is applied by the fastening member, the impeller case side abutting surface including an impeller case side first abutting surface abutting against the fastening member and an impeller case side second abutting surface abutting against the bearing case,
the bearing housing has a bearing housing side abutting surface extending in a direction intersecting with an axial direction of the rotary shaft at the fastening portion, the bearing housing side abutting surface includes a bearing housing side first abutting surface abutting against the fastening member and a bearing housing side second abutting surface abutting against the impeller housing,
the fastening member has a fastening member side abutment surface extending in a direction intersecting with an axial direction of the rotary shaft, the fastening member side abutment surface includes a fastening member side first abutment surface abutting the impeller housing and a fastening member side second abutment surface abutting the bearing housing,
at least one of a portion between the impeller housing side first abutting surface and the fastening member side first abutting surface, a portion between the bearing housing side first abutting surface and the fastening member side second abutting surface, and a portion between the impeller housing side second abutting surface and the bearing housing side second abutting surface is provided with a thin plate member configured separately from the impeller housing, the bearing housing, and the fastening member.
According to the configuration of the above (1), since the thin plate member is provided between the two contact surfaces formed by the impeller housing, the bearing housing, and the fastening member, the contact portion between the two contact surfaces increases, and thus minute relative vibration (minute vibration in the direction along the contact surfaces) is generated between the two contact surfaces. Thus, friction is generated between the two contact surfaces, and shaft vibration from the rotating shaft is attenuated by the friction attenuation action, so that vibration and noise generated in the rotating machine can be suppressed.
(2) In some embodiments, in the structure of (1) above,
at least one of the impeller housing side first abutting surface, the impeller housing side second abutting surface, the bearing housing side first abutting surface, the bearing housing side second abutting surface, the fastening member side first abutting surface, and the fastening member side second abutting surface has at least one recess.
According to the configuration of the above (2), since at least one surface of the contact surface has the concave portion, the contact area between the thin plate member and the contact surface is reduced, and when vibration occurs, fine vibration (fine vibration in a direction intersecting the contact surface) is likely to occur between the thin plate member and the contact surface in addition to the above-described fine relative vibration. When a slight rattling motion occurs between the contact surfaces, the shaft vibration from the rotary shaft is damped by the collision damping action. Therefore, vibration and noise generated in the rotary machine can be further suppressed.
(3) In some embodiments, in the structure of (2) above,
the at least one recess includes a plurality of recesses provided at intervals in a circumferential direction of the rotary shaft.
According to the configuration of the above (3), the effect of damping vibration can be further improved by the friction damping action and the collision damping action of the plurality of concave portions formed in the circumferential direction of the rotating shaft.
(4) In some embodiments, in the structure of (2) or (3) above,
the at least one recess is formed in at least one of the two abutment surfaces constituting at least one of the positions between the impeller-housing-side first abutment surface and the fastening-member-side first abutment surface where the thin plate member is located, between the bearing-housing-side first abutment surface and the fastening-member-side second abutment surface, and between the impeller-housing-side second abutment surface and the bearing-housing-side second abutment surface.
According to the configuration of the above (4), the recessed portion is formed in at least one of the two contact surfaces where the thin plate member is located, and the vibration damping effect can be further improved by a combined effect of a friction damping effect of friction generated between the thin plate member and the contact surfaces and a friction damping effect and a collision damping effect by the presence of the recessed portion.
(5) In some embodiments, in any of the structures (1) to (4) above,
the impeller housing has an impeller housing side flange portion extending radially outward of the rotary shaft,
the bearing housing has a bearing housing side flange portion that abuts the impeller housing side flange portion, the bearing housing side flange portion extending radially outward of the rotary shaft,
the impeller housing side second abutting surface is formed on the impeller housing side flange portion, and the bearing housing side second abutting surface is formed on the bearing housing side flange portion,
the fastening member is a connecting mechanism (カップリング) that sandwiches the impeller housing side flange portion and the bearing housing side flange portion.
According to the configuration of the above (5), in the rotary machine in which the fastening member is the coupling mechanism that sandwiches the impeller housing side flange portion and the bearing housing side flange portion, vibration and noise generated in the rotary machine can be suppressed.
In addition, since the existing contact surface is used, there is no need to modify the rotary machine.
(6) In some embodiments, in the structure of (5) above,
the thin plate member is a single thin plate member, and is positioned between the impeller housing side first abutting surface and the fastening member side first abutting surface, and between the bearing housing side first abutting surface and the fastening member side second abutting surface.
According to the configuration of the above (6), in addition to the operational effect of the configuration of the above (5), the vibration damping effect can be improved by providing the thin plate member between the two contact surfaces to which the pressing force is applied by the connection mechanism. Further, since the thin plate member is formed of one thin plate member, the manufacturing is easy, and the clamping between the contact surfaces is easy.
(7) In some embodiments, in any of the structures (1) to (4) above,
the impeller housing has an impeller housing side projection extending radially inward of the rotary shaft,
the bearing housing has a bearing housing-side projection that abuts the impeller housing-side projection, the bearing housing-side projection extending radially outward of the rotary shaft,
the impeller-housing-side second abutment surface is formed on the impeller-housing-side protrusion, and the bearing-housing-side second abutment surface is formed on the bearing-housing-side protrusion,
the fastening member is a snap ring (スナップリング) fitted into an annular groove formed in an inner peripheral surface of the impeller housing, and the outer peripheral portion of the snap ring is fitted into the annular groove to urge the bearing housing side second contact surface toward the impeller housing side second contact surface.
According to the configuration of the above (7), in the rotary machine in which the fastening member is the snap ring configured to urge the bearing housing side second contact surface toward the impeller housing side second contact surface, it is possible to suppress vibration and noise generated in the rotary machine.
In addition, since the existing contact surface is used, there is no need to modify the rotary machine.
(8) In some embodiments, in the structure of (7) above,
the thin plate member is located between the impeller-housing-side second abutting surface and the bearing-housing-side second abutting surface.
According to the configuration of the above (8), in addition to the operational effect of the configuration of the above (7), the vibration damping effect can be improved by providing the thin plate member between the two contact surfaces to which the pressing force is applied by the snap ring.
(9) In some embodiments, in the structure of (7) above,
the thin plate member is located between the fastening member-side second abutment surface and the bearing housing-side first abutment surface.
According to the configuration of the above (9), in addition to the operational effect of the configuration of the above (7), the vibration damping effect can be improved by providing the thin plate member between the two abutment surfaces to which the pressing force is applied by the snap ring.
(10) In some embodiments, in any of the structures (1) to (4) above,
the bearing housing has a bearing housing side extension extending radially outward of the rotary shaft,
the impeller housing has an impeller housing-side bolt receiving portion located further to the radially outer side of the rotary shaft than the bearing housing-side extension portion, and an impeller housing-side extension portion abutting against the bearing housing-side extension portion and extending from the impeller housing-side bolt receiving portion to the radially inner side of the rotary shaft,
the impeller-housing-side second abutment surface is formed on the impeller-housing-side extension, and the bearing-housing-side second abutment surface is formed on the bearing-housing-side extension,
the fastening member is a bolt screwed into a screw hole formed in the impeller housing-side bolt receiving portion, and biases the bearing housing-side second contact surface toward the impeller housing-side second contact surface by being screwed into the screw hole.
According to the configuration of the above (10), in the rotary machine in which the fastening member is the bolt configured to urge the bearing housing side second contact surface toward the impeller housing side second contact surface, it is possible to suppress vibration and noise generated in the rotary machine.
In addition, since the existing contact surface is used, there is no need to modify the rotary machine.
(11) In some embodiments, in the structure of (10) above,
the thin plate member is located between the impeller-housing-side second abutting surface and the bearing-housing-side second abutting surface.
According to the configuration of the above (11), the vibration damping effect can be improved by providing the thin plate member between the two contact surfaces to which the pressing force is applied by the bolt.
(12) Some embodiments provide a rotary machine, comprising:
a rotating shaft;
an impeller attached to the rotating shaft;
an impeller housing that houses the impeller;
a bearing housing that houses a bearing that rotatably supports the rotating shaft and is fastened to the impeller housing;
a fastening member that fastens the impeller housing and the bearing housing in an axial direction of the rotary shaft,
the impeller case has an impeller case side abutting surface extending in a direction intersecting an axial direction of the rotary shaft at a fastening portion to which a fastening force is applied by the fastening member, the impeller case side abutting surface including an impeller case side first abutting surface abutting against the fastening member and an impeller case side second abutting surface abutting against the bearing case,
the bearing housing has a bearing housing side abutting surface extending in a direction intersecting with an axial direction of the rotary shaft at the fastening portion, the bearing housing side abutting surface includes a bearing housing side first abutting surface abutting against the fastening member and a bearing housing side second abutting surface abutting against the impeller housing,
the fastening member has a fastening member side abutment surface extending in a direction intersecting with an axial direction of the rotary shaft, the fastening member side abutment surface includes a fastening member side first abutment surface abutting the impeller housing and a fastening member side second abutment surface abutting the bearing housing,
at least one of the impeller-housing-side first abutting surface, the impeller-housing-side second abutting surface, the bearing-housing-side first abutting surface, the bearing-housing-side second abutting surface, the fastening-member-side first abutting surface, and the fastening-member-side second abutting surface has at least one recess.
According to the configuration of the above (12), since at least one of the abutting surfaces between the two abutting surfaces formed by the impeller housing, the bearing housing, and the fastening member has at least one concave portion, minute relative vibration (minute vibration in the direction along the abutting surface) and minute shaking (minute vibration in the direction intersecting the abutting surface) are likely to occur between the two abutting surfaces. When minute relative vibration occurs between the contact surfaces, friction occurs between the two contact surfaces, and shaft vibration from the rotating shaft is attenuated by the friction attenuation action. When a slight rattling motion occurs between the contact surfaces, the shaft vibration from the rotary shaft is damped by the collision damping action. This can suppress vibration and noise generated in the rotary machine.
(13) In some embodiments, in the structure of (12) above,
the at least one recess includes a plurality of recesses provided at intervals in a circumferential direction of the rotary shaft.
According to the configuration of the above (13), the effect of damping vibration can be further improved by the collision damping action of the plurality of concave portions formed in the circumferential direction of the rotating shaft.
(14) In some embodiments, in the structure of the above (12) or (13),
the impeller housing has an impeller housing side projection extending radially inward of the rotary shaft,
the bearing housing has a bearing housing-side projection that abuts the impeller housing-side projection, the bearing housing-side projection extending radially outward of the rotary shaft,
the impeller-housing-side second abutment surface is formed on the impeller-housing-side protrusion, and the bearing-housing-side second abutment surface is formed on the bearing-housing-side protrusion,
the fastening member is a snap ring fitted into an annular groove formed in an inner peripheral surface of the impeller housing, and the outer peripheral portion of the snap ring is fitted into the annular groove to apply a force to the bearing housing side second contact surface toward the impeller housing side second contact surface.
According to the configuration of the above (14), in the rotary machine in which the fastening member is the snap ring configured to urge the bearing housing side second contact surface toward the impeller housing side second contact surface, vibration and noise generated in the rotary machine can be suppressed.
In addition, since the existing contact surface is used, there is no need to modify the rotary machine.
(15) In some embodiments, in the structure of the above (12) or (13),
the bearing housing has a bearing housing side extension extending radially outward of the rotary shaft,
the impeller housing has an impeller housing-side bolt receiving portion located further to the radially outer side of the rotary shaft than the bearing housing-side extension portion, and an impeller housing-side extension portion abutting against the bearing housing-side extension portion and extending from the impeller housing-side bolt receiving portion to the radially inner side of the rotary shaft,
the impeller-housing-side second abutment surface is formed on the impeller-housing-side extension, and the bearing-housing-side second abutment surface is formed on the bearing-housing-side extension,
the fastening member is a bolt screwed into a screw hole formed in the impeller housing-side bolt receiving portion, and biases the bearing housing-side second contact surface toward the impeller housing-side second contact surface by being screwed into the screw hole.
According to the configuration of the above (15), in the rotary machine in which the fastening member is the bolt configured to urge the bearing housing side second contact surface toward the impeller housing side second contact surface, it is possible to suppress vibration and noise generated in the rotary machine.
In addition, since the existing contact surface is used, there is no need to modify the rotary machine.
Effects of the invention
According to some embodiments, vibration of a rotary machine can be reduced by a simple and low-cost structure, and thus, noise generated in the rotary machine can be suppressed.
Drawings
Fig. 1 is a front sectional view of a turbocharger of one embodiment.
Fig. 2 is a front sectional view showing a part of a turbocharger according to an embodiment.
Fig. 3 is an enlarged cross-sectional view of a part (corresponding to a portion a in fig. 2) of the turbocharger according to the embodiment.
Fig. 4 is an enlarged cross-sectional view of a part (corresponding to a portion B in fig. 2) of the turbocharger according to the embodiment.
Fig. 5 is an enlarged cross-sectional view of a part (corresponding to a portion B in fig. 2) of the turbocharger according to the embodiment.
Fig. 6 is a front sectional view showing a part of a turbocharger according to an embodiment.
Fig. 7 is an enlarged sectional view of a part (corresponding to a portion C in fig. 6) of the turbocharger according to the embodiment.
Fig. 8 is a sectional view of a recess in some embodiments of (a), (B), and (C).
Fig. 9 is a front sectional view showing a part of a turbocharger according to an embodiment.
Fig. 10 is an enlarged cross-sectional view of a part (corresponding to a portion a in fig. 2) of the turbocharger according to the embodiment.
Fig. 11 is an enlarged cross-sectional view of a part (corresponding to a portion B in fig. 2) of the turbocharger according to the embodiment.
Fig. 12 is a front view of a snap ring (fastening member) of an embodiment.
Fig. 13 is a diagram showing a noise generation state according to an embodiment.
Fig. 14 is a front sectional view of a snap ring (fastening member) according to an embodiment.
Fig. 15 is a diagram showing a noise generation state according to an embodiment.
Detailed Description
Some embodiments of the present invention are described below with reference to the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the constituent components described as the embodiments and shown in the drawings are not intended to limit the scope of the present invention to these, and are merely illustrative examples.
For example, a relative or absolute arrangement expression such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "central", "concentric", or "coaxial" indicates not only a strict arrangement but also a state of being relatively displaced by an angle and a distance to the extent of tolerance or obtaining the same function.
For example, the expression "the same", "equal", and "uniform" indicate that the same objects are equal to each other, and that the objects are different from each other in terms of tolerance or obtaining the same function, as well as the states of strict equality.
For example, the expression indicating the shape such as a square shape or a cylindrical shape indicates not only the shape such as a square shape or a cylindrical shape in a strict geometrical sense but also a shape including a concave and convex portion, a chamfered portion, or the like within a range in which the same effect is obtained.
On the other hand, the expression "provided with", "having", "provided with", "including" or "provided with" one constituent element is not an exclusive expression other than the presence of other constituent elements.
As shown in fig. 1, the rotary machine 10 includes: a rotary shaft 12, impellers 14(14a, 14b) attached to the rotary shaft 12, impeller housings 16(16a, 16b) that house the impellers 14(14a, 14b), and a bearing housing 18. The bearing housing 18 accommodates a bearing 19 that rotatably supports the rotary shaft 12, and is fastened to the impeller housing 16. The impeller housing 16 and the bearing housing 18 are fastened in the axial direction of the rotary shaft 12 by fastening members 20(20a, 20b, 20 c). That is, the tightening members 20(20a, 20b, 20c) apply a tightening force in the axial direction of the rotary shaft 12 to the impeller housing 16 and the bearing housing 18.
In the illustrated embodiment, the rotary machine 10 is a turbocharger mounted in an automobile or the like, and a compressor impeller 14(14a) and a turbine impeller 14(14b) are mounted on both end regions of the rotary shaft 12. The compressor impeller 14(14a) is housed in the compressor housing 16(16a), and the turbine impeller 14(14b) is housed in the turbine housing 16(16 b). Between these housings, a bearing housing 18 is provided, and the compressor housing 16(16a) and the bearing housing 18 are axially fastened by a coupling mechanism 22(22a), and the turbine housing 16(16b) and the bearing housing 18 are axially fastened by a snap ring 22(22 b).
In the illustrated embodiment, the turbine wheel 14(14b) is rotated by exhaust gas e discharged from an engine (not illustrated) through the turbine housing 16(16 b). The intake air a is sucked into the compressor housing 16(16a) by the compressor impeller 14(14a) on the rotary shaft 12, compressed in the compressor housing 16(16a), and sent to the engine.
When the rotary machine 10 is operated, the vibration of the rotary shaft 12 propagates to each housing as indicated by an arrow, and each housing vibrates, so that radiation noise may be generated.
In some embodiments, as shown in fig. 2 to 7, in the fastening portion 20(20a, 20b, 20c, 20d) that applies fastening force in the rotation axis direction by the fastening member 22(22a, 22b, 22c), the impeller housing 16 has an impeller housing side abutment surface 24(24a, 24b) that extends in a direction intersecting with the axial direction of the rotation axis 12. The impeller housing side abutment surface 24 includes an impeller housing side first abutment surface 24(24a) that abuts the fastening member 22 and an impeller housing side second abutment surface 24(24b) that abuts the bearing housing 18.
The bearing housing 18 has a bearing-housing-side abutment surface 26(26a, 26b) extending in a direction intersecting the axial direction of the rotary shaft 12 at the fastening portion 20. The bearing-housing-side contact surface 26 includes a bearing-housing-side first contact surface 26(26a) that contacts the fastening member 22, and a bearing-housing-side second contact surface 26(26b) that contacts the impeller housing 16.
The tightening member 22 has tightening member-side abutment surfaces 28(28a, 28b) extending in a direction intersecting the axial direction of the rotary shaft 12. The fastening member side contact surface 28 includes a fastening member side first contact surface 28(28a) that contacts the impeller housing 16 and a fastening member side second contact surface 28(28b) that contacts the bearing housing 18.
Further, thin plate members 30(30a, 30b, 30c, 30d) are provided at least at one of positions between the impeller-housing-side first abutment surface 24(24a) and the fastening-member-side first abutment surface 28(28a), between the bearing-housing-side first abutment surface 26(26a) and the fastening-member-side second abutment surface 28(28b), and between the impeller-housing-side second abutment surface 24(24b) and the bearing-housing-side second abutment surface 26(26 b). The thin plate member 30 is formed separately from the impeller housing 16, the bearing housing 18, and the fastening member 22.
The thin plate member 30 is not particularly limited, and for example, a metal or heat-resistant resin plate member having a plate thickness of 0.1mm to 2.0mm, preferably 0.5mm to 1.0mm, or the like can be used.
According to the above configuration, since the thin plate member 30 is provided between the two contact surfaces formed by the impeller housing 16, the bearing housing 18, and the fastening member 22, the contact portion between the two contact surfaces increases, and therefore, a minute relative vibration (a minute vibration in the direction along the contact surface) is generated between the two contact surfaces. As a result, friction is generated between the two contact surfaces, and shaft vibration from the rotating shaft 12 is attenuated by the friction attenuation effect, so that vibration and noise generated in the rotary machine 10 can be suppressed.
Further, the vibration of the rotary shaft 12, which causes the vibration of the rotary machine 10, is caused by the imbalance of the weight of the rotary shaft 12, and the like. Therefore, the vibration of the rotary machine 10 is suppressed by the above configuration, and the allowable unbalance value of the rotary shaft 12 can be reduced, thereby improving the manufacturing yield of the rotary shaft 12.
In the turbocharger of the embodiment shown in fig. 1, the tightening force between the impeller housing 16, the bearing housing 18, and the tightening member 22 is less strong as the radial direction of the rotation axis is toward the rotation axis. Therefore, a positional deviation in the radial direction of the rotation axis is relatively likely to occur between the two contact surfaces between which the thin plate member 30 is provided, and the frictional force generated by the positional deviation improves the vibration damping effect of the turbocharger.
In one embodiment, as shown in fig. 3, the impeller housing 16 has an impeller housing side flange portion 34 extending radially outward of the rotary shaft 12, and the bearing housing 18 has a bearing housing side flange portion 36 abutting against the impeller housing side flange portion 34 and extending radially outward of the rotary shaft 12.
The impeller-housing-side second abutment surface 24(24b) is formed on the impeller-housing-side flange portion 34, and the bearing-housing-side second abutment surface 26(26b) is formed on the bearing-housing-side flange portion 36.
The fastening member 22(22a) is a connecting mechanism that sandwiches the impeller housing side flange portion 34 and the bearing housing side flange portion 36.
Further, the impeller-housing-side first abutment surface 24(24a), the impeller-housing-side second abutment surface 24(24b), the bearing-housing-side first abutment surface 26(26a), the bearing-housing-side second abutment surface 26(26b), the fastening-member-side first abutment surface 28(28a), and the fastening-member-side second abutment surface 28(28b) extend in a direction intersecting the rotation axis direction.
According to the above configuration, in the rotary machine in which the fastening member 22(22a) is the coupling mechanism that sandwiches the impeller housing side flange portion 34 and the bearing housing side flange portion 36, vibration and noise generated in the rotary machine 10 can be suppressed.
Further, since the two abutment surfaces existing in the conventional fastening portion 20(20a) are used, the modification of the rotary machine 10 is not required.
In the illustrated embodiment, the impeller housing side flange portion 34 is a flange portion formed in the turbine housing 16(16b), and the fastening member 22(22a) is an annular coupling mechanism member (V coupling mechanism) having both side portions bent in the cross section, and the impeller housing side flange portion 34 and the bearing housing side flange portion 36 are sandwiched by the bent portions.
Since the impeller-housing-side second contact surface 24(24b) and the bearing-housing-side second contact surface 26(26b) extend in the rotation axis radial direction, the vibration damping effect of the rotary machine 10 can be improved by the positional deviation in the rotation axis radial direction, as described above.
In one embodiment, as shown in fig. 3, the thin plate member 30(30a) is formed of one thin plate member, and is provided between the impeller-housing-side first contact surface 24(24a) and the fastening-member-side first contact surface 28(28a), and between the bearing-housing-side first contact surface 26(26a) and the fastening-member-side second contact surface 28(28 b).
In addition to the above-described operational effects, the vibration damping effect can be improved by providing the thin plate member 30(30a) between the two contact surfaces to which the pressing force is applied by the connecting mechanism 22(22a), and the thin plate member 30(30a) is formed of one thin plate member, so that the manufacturing is easy and the sandwiching between the two contact surfaces is easy.
In the illustrated embodiment, the thin plate member 30(30a) has a ring shape, conforms to the inner surface of the fastening member 22(22a) in cross section, and has a shape curved on both sides so as to surround the impeller-housing-side flange portion 34 and the bearing-housing-side flange portion 36. This can facilitate the arrangement in the narrow space between the fastening member 22(22a) and the impeller housing side flange portion 34 and the bearing housing side flange portion 36.
In one embodiment, as shown in fig. 4, the impeller housing 16 has an impeller housing-side projection 38 extending radially inward of the rotary shaft 12, and the bearing housing 18 has a bearing housing-side projection 40 extending radially outward of the rotary shaft 12 and abutting against the impeller housing-side projection 38.
The impeller-housing-side second abutment surface 24(24b) is formed on the impeller-housing-side protrusion 38, and the bearing-housing-side second abutment surface 26(26b) is formed on the bearing-housing-side protrusion 40.
The fastening member 22(22b) is formed of a snap ring, and an outer peripheral portion of the snap ring is fitted into an annular groove 41 formed along an inner peripheral surface of the impeller housing 16. The bearing housing side second contact surface 26(26b) is biased toward the impeller housing side second contact surface 24(24b) by the snap ring 22(22 b).
According to the above configuration, in the rotary machine 10 in which the fastening member 22(22b) is the snap ring that biases the bearing-housing-side second contact surface 26(26b) against the impeller-housing-side second contact surface 24(24b), vibration and noise generated in the rotary machine 10 can be suppressed.
Further, since the two abutment surfaces existing in the conventional fastening portion 20(20b) are used, the modification of the rotary machine 10 is not required.
In one embodiment, as shown in fig. 4, the thin plate member 30(30b) is located between the impeller-housing-side second abutment surface 24(24b) and the bearing-housing-side second abutment surface 26(26 b).
According to the above configuration, in addition to the above operation and effect, the thin plate member 30(30b) is provided between the two contact surfaces to which the pressing force is applied by the snap ring 22(22b), so that the vibration damping effect of the rotary machine 10 can be improved.
In the illustrated embodiment, the two contact surfaces extend in the radial direction of the rotation axis, and therefore, as described above, the vibration damping effect of the rotary machine 10 can be improved by utilizing the positional deviation in the radial direction of the rotation axis.
In the illustrated embodiment, as shown in fig. 4, the impeller housing 16 is a turbine housing 16(16b), and the impeller-housing-side projection 38 is formed on the turbine housing 16(16 b).
The end surface 38b of the turbine housing 16(16b) other than the top surface 38a and the top surface 38a of the impeller housing-side projecting portion 38 forms an annular step surface having different distances from the rotary shaft 12 along the rotary shaft direction. The top surface 40a of the bearing-housing-side protrusion 40 and the end surface 40b of the bearing housing 18 other than the top surface 40a form annular stepped surfaces having different distances from the rotary shaft 12 along the axial direction of the rotary shaft 12.
The thin plate member 30(30b) is integrally formed of a first annular portion 42 provided between the top surface 38a and the end surface 40b and extending in the axial direction of the rotary shaft 12, a disk portion 44 provided between the impeller-housing-side second contact surface 24(24b) and the bearing-housing-side second contact surface 26(26b) and extending in the radial direction of the rotary shaft 12, and a second annular portion 46 provided between the top surface 40a and the end surface 38 b. Further, a seal 47 is interposed between the first annular portion 42 and the bearing housing 18.
With the above configuration, the contact surfaces between the thin plate member 30(30b), the impeller-housing-side second contact surface 24(24b), and the bearing-housing-side second contact surface 26(26b) increase in area, and the frictional force between these contact surfaces increases, so that the vibration damping effect of the rotary machine 10 can be improved.
In one embodiment, as shown in fig. 5, the thin plate member 30(30c) is provided between the fastening member-side second abutment surface 28(28b) and the bearing housing-side first abutment surface 26(26 a).
According to the above configuration, the thin plate member 30(30c) is provided between the two contact surfaces to which the pressing force is applied by the snap ring 22(22b), whereby the vibration damping effect of the rotary machine 10 can be improved. Further, since the thin plate member 30(30c) is disposed between the two abutment surfaces existing in the conventional fastening portion 20(20c), the modification of the rotary machine 10 is not required.
In the illustrated embodiment, the fastening member-side second contact surface 28(28b) and the bearing housing-side second contact surface 26(26b) extend in the radial direction of the rotation shaft, and the thin plate member 30(30c) is disposed in the radial direction of the rotation shaft 12 and has a disk shape extending in the circumferential direction of the rotation shaft 12. Therefore, the relative positional deviation between the fastening member-side second contact surface 28(28b) and the bearing housing-side first contact surface 26(26a) in the radial direction of the rotation axis during operation of the rotary machine 10 becomes easy, and therefore, the frictional force increases between these two contact surfaces, and the vibration damping effect of the rotary machine 10 can be improved. In addition, the thin plate member 30(30c) has a simple shape, and therefore can be manufactured at low cost.
In one embodiment, as shown in fig. 6 and 7, the bearing housing 18 has a bearing housing-side extension 48 extending radially outward of the rotary shaft 12. The impeller housing 16 has an impeller housing-side bolt receiving portion 50 and an impeller housing-side extending portion 52, the impeller housing-side bolt receiving portion 50 is located further to the radially outer side of the rotary shaft 12 than the bearing housing-side extending portion 48, and the impeller housing-side extending portion 52 abuts against the bearing housing-side extending portion 48 and extends from the impeller housing-side bolt receiving portion 50 to the radially inner side of the rotary shaft 12.
The impeller-housing-side second abutment surface 24(24b) is formed on the impeller-housing-side extension 52, and the bearing-housing-side second abutment surface 26(26b) is formed on the bearing-housing-side extension 48. The impeller housing side second abutment surface 24(24b) and the bearing housing side second abutment surface 26(26b) extend in a direction intersecting the rotation axis direction.
The fastening member 22(22c) is a bolt that is screwed into a threaded hole 54 formed in the impeller housing-side bolt receiving portion 50. The bolt 22(22c) is screwed into the screw hole 54, and biases the bearing-housing-side second contact surface 26(26b) toward the impeller-housing-side second contact surface 24(24 b).
According to the above configuration, in the rotary machine 10 in which the fastening member 22(22c) is a bolt configured to urge the bearing-housing-side second contact surface 26(26b) toward the impeller-housing-side second contact surface 24(24b), it is possible to suppress vibration and noise generated in the rotary machine 10.
Further, since the two contact surfaces existing in the conventional fastening portion 20(20d) are used, the modification of the rotary machine 10 is not required.
In one embodiment, as shown in fig. 7, a thin plate member 30(30d) is provided between the impeller-housing-side second abutment surface 24(24b) and the bearing-housing-side second abutment surface 26(26 b).
According to the above configuration, the thin plate member 30(30d) is provided between the two contact surfaces to which the pressing force is applied by the bolt 22(22c), whereby the vibration damping effect of the rotary machine 10 can be improved.
In the illustrated embodiment, the impeller-housing-side second contact surface 24(24b) and the bearing-housing-side second contact surface 26(26b) extend in the radial direction of the rotation axis, so that, during operation of the rotary machine 10, positional deviation between these contact surfaces becomes easy, and this positional deviation increases the frictional force, thereby making it possible to improve the vibration damping effect of the rotary machine 10.
Further, a washer 56 is interposed between the head of the bolt 22(22c) and the impeller-housing-side bolt receiving portion 50, and a spring force applied to the impeller-housing-side extending portion 52 with respect to the bearing-housing-side extending portion 48 is applied by the washer 56. This increases the spring force against the bearing housing side second contact surface 26(26b), and increases the frictional force generated between the impeller housing side first contact surface 24(24a) and the bearing housing side second contact surface 26(26 b).
Further, instead of using the washer 56, the elastic force may be applied to the bearing-housing-side extension 48 only by the head of the bolt 22(22 c).
In some embodiments, in the rotary machine 10 shown in fig. 2 to 7, at least one of the impeller-housing-side first abutment surface 24(24a), the impeller-housing-side second abutment surface 24(24b), the bearing-housing-side first abutment surface 26(26a), the bearing-housing-side second abutment surface 26(26b), the fastening-member-side first abutment surface 28(28a), and the fastening-member-side second abutment surface 28(28b) has at least one recessed portion 32(32a, 32b, 32c) as shown in fig. 8.
According to the above configuration, since at least one surface of each of the two contact surfaces has the concave portion 32, the contact area between the thin plate member 30 and the contact surface is reduced, and when vibration occurs, slight shaking (slight vibration in a direction intersecting the contact surface) is likely to occur between the thin plate member 30 and the contact surface. When a slight rattling motion occurs between the contact surfaces, the shaft vibration from the rotary shaft 12 is damped by the collision damping action. This can further suppress vibration and noise generated in the rotary machine 10.
In some embodiments, as shown in fig. 8, the recess 32 formed in at least one of the respective two abutment surfaces includes a plurality of recesses 32 provided at intervals in the circumferential direction of the rotary shaft 12.
According to this configuration, the impact damping effect of the plurality of recesses 32 formed in the circumferential direction of the rotary shaft 12 can be further improved.
In one embodiment, as shown in fig. 8(a), the recesses 32(32a) are formed by a plurality of recesses having flat surfaces at equal intervals along the circumferential direction of the rotary shaft 12. Convex portions 33(33a) having a flat surface are formed between the concave portions 32(32 a).
In another embodiment shown in fig. 8(B), the concave portions 32(32B) are formed at equal intervals between the convex portions 33(33B) formed in a wave-shaped cross section.
In still another embodiment shown in fig. 8(C), in a cross section in which a plurality of circular arcs are formed at equal intervals, the concave portions 32(32C) are formed at equal intervals between the circular arcs.
In some embodiments, in the rotary machine 10 shown in fig. 2 to 7, the thin plate member 30 is provided at least one of between the impeller-housing-side first abutment surface 24(24a) and the fastening-member-side first abutment surface 28(28a), between the bearing-housing-side first abutment surface 26(26a) and the fastening-member-side second abutment surface 28(28b), and between the impeller-housing-side second abutment surface 24(24b) and the bearing-housing-side second abutment surface 26(26 b). Further, a concave portion 32 as shown in fig. 8 is formed on at least one of the two contact surfaces between which the thin plate member 30 is located.
According to the above configuration, since the concave portion 32 is formed on at least one of the two contact surfaces between which the thin plate member 30 is located, the vibration damping effect can be further improved by a combined effect of the friction damping action generated by the friction between the thin plate member 30 and the contact surfaces and the friction damping action and the collision damping action due to the presence of the concave portion 32.
In some embodiments, as shown in fig. 1, the present invention includes: a rotary shaft 12, impellers 14(14a, 14b) attached to the rotary shaft 12, impeller housings 16(16a, 16b) that house the impellers 14(14a, 14b), and a bearing housing 18. The bearing housing 18 accommodates a bearing 19 that rotatably supports the rotary shaft 12, and is fastened to the impeller housing 16. The impeller housing 16 and the bearing housing 18 are fastened in the axial direction of the rotary shaft 12 by fastening members 20(20a, 20b, 20 c).
As shown in fig. 9 to 11, in the fastening portion 20 to which the fastening force is applied in the rotation axis direction by the fastening member 22, the impeller housing 16 has impeller housing side abutment surfaces 24(24a, 24b) extending in a direction intersecting with the axial direction of the rotation axis 12. The impeller housing side abutting surface 24 includes an impeller housing side first abutting surface 24(24a) abutting against the fastening member 22, and an impeller housing side second abutting surface 24(24b) abutting against the bearing housing 18.
The bearing housing 18 has a bearing-housing-side abutment surface 26(26a, 26b) extending in a direction intersecting the axial direction of the rotary shaft 12 at the fastening portion 20. The bearing-housing-side contact surface 26 includes a bearing-housing-side first contact surface 26(26a) that contacts the fastening member 22, and a bearing-housing-side second contact surface 26(26b) that contacts the impeller housing 16.
The tightening member 22 has tightening member-side abutment surfaces 28(28a, 28b) extending in a direction intersecting the axial direction of the rotary shaft 12. The fastening member side contact surface 28 includes a fastening member side first contact surface 28(28a) that contacts the impeller housing 16, and a fastening member side second contact surface 28(28b) that contacts the bearing housing 18.
As shown in fig. 9 to 11, at least one of the impeller-housing-side first contact surface 24(24a), the impeller-housing-side second contact surface 24(24b), the bearing-housing-side first contact surface 26(26a), the bearing-housing-side second contact surface 26(26b), the fastening-member-side first contact surface 28(28a), and the fastening-member-side second contact surface 28(28b) has at least one recess 32(32a, 32b, 32 c).
According to the above configuration, by providing at least one recess 32 in at least one of the two contact surfaces formed by the impeller housing 16, the bearing housing 18, and the fastening member 22, a slight relative vibration (a slight vibration in the direction along the contact surface) and a slight rattling (a slight vibration in the direction intersecting the contact surface) are likely to occur between the two contact surfaces. When minute relative vibration occurs between the contact surfaces, friction occurs between the two contact surfaces, and shaft vibration from the rotary shaft 12 is attenuated by the friction attenuation action. When a slight rattling motion occurs between the contact surfaces, the shaft vibration from the rotary shaft 12 is damped by the collision damping action. This can suppress vibration and noise generated in the rotary machine 10.
Further, the vibration of the rotary shaft 12, which causes the vibration of the rotary machine 10, is caused by the imbalance of the weight of the rotary shaft 12, and the like. With this configuration, since the vibration of the rotary machine 10 can be suppressed, the allowable unbalance value of the rotary shaft 12 can be reduced, and the manufacturing yield of the rotary shaft 12 can be improved.
In one embodiment, as shown in fig. 9, the fastening member 22(22a) is a connecting mechanism that sandwiches the impeller housing side flange portion 34 and the bearing housing side flange portion 36. In this embodiment, at least one of the impeller-housing-side first abutment surface 24(24a), the impeller-housing-side second abutment surface 24(24b), the bearing-housing-side first abutment surface 26(26a), the bearing-housing-side second abutment surface 26(26b), the fastening-member-side first abutment surface 28(28a), and the fastening-member-side second abutment surface 28(28b) has at least one recess 32.
According to the above configuration, in the rotary machine in which the fastening member 22(22a) is the coupling mechanism that sandwiches the impeller housing side flange portion 34 and the bearing housing side flange portion 36, vibration and noise generated in the rotary machine 10 can be suppressed.
Further, by forming the concave portion 32 on at least one of the two contact surfaces to which the pressing force is applied by the connection mechanism 20(20a), the vibration damping effect can be improved. Further, since the concave portion 32 is formed in the two abutment surfaces existing in the conventional fastening portion 20(20a), the modification of the rotary machine 10 is not required.
In one embodiment, as shown in fig. 10(a), the fastening member 22(22b) is a snap ring that fastens the impeller housing 16 and the bearing housing 18 in the axial direction of the rotary shaft 12. In this embodiment, at least one of the impeller-housing-side first abutment surface 24(24a), the impeller-housing-side second abutment surface 24(24b), the bearing-housing-side first abutment surface 26(26a), the bearing-housing-side second abutment surface 26(26b), the fastening-member-side first abutment surface 28(28a), and the fastening-member-side second abutment surface 28(28b) has at least one recess 32.
According to the above configuration, in the rotary machine 10 in which the fastening member 22(22b) is the snap ring configured to urge the bearing-housing-side second contact surface 26(26b) toward the impeller-housing-side second contact surface 24(24b), it is possible to suppress vibration and noise generated in the rotary machine 10.
Further, by forming the concave portion 32 on at least one of the two contact surfaces to which the pressing force is applied by the snap ring 22(22b), the vibration damping effect can be improved.
Further, since the recess 32 is formed in the two abutment surfaces existing in the conventional fastening portion 20(20b), the modification of the rotary machine 10 is not required.
In the illustrated embodiment, the impeller housing 16 is a turbine housing 16(16b), and the recess 32 is formed in the impeller-housing-side first contact surface 24(24a), the impeller-housing-side second contact surface 24(24b), and the bearing-housing-side first contact surface 26(26 a).
Fig. 10B shows an example in which a plurality of recesses 32(32a) are formed in the bearing-housing-side first contact surface 26(26a) at intervals in the circumferential direction of the rotary shaft 12.
In this way, in the tightening portion 20(20c), the recess 32(32a) is formed in the abutment surface of 3 portions, and thus the vibration damping effect of the rotary machine 10 can be improved.
In one embodiment, as shown in FIG. 11, the bearing housing 18 has a bearing housing side extension 48 that extends radially outward of the axis of rotation. The impeller housing 16 has an impeller housing-side bolt receiving portion 50 and an impeller housing-side extending portion 52, the impeller housing-side bolt receiving portion 50 is located further toward the outer side in the radial direction of the rotation shaft than the bearing housing-side extending portion 48, and the impeller housing-side extending portion 52 abuts against the bearing housing-side extending portion 48 and extends from the impeller housing-side bolt receiving portion 50 toward the inner side in the radial direction of the rotation shaft.
The impeller-housing-side second abutment surface 24(24b) is formed on the impeller-housing-side extension 52, and the bearing-housing-side second abutment surface 26(26b) is formed on the bearing-housing-side extension 48.
The fastening member 22(22c) is a bolt screwed into a threaded hole 54 formed in the impeller housing-side bolt receiving portion 50, and the bearing housing-side second contact surface 26(26b) is urged toward the impeller housing-side second contact surface 24(24b) by the bolt being screwed into the threaded hole 54. A recess 32 is formed in at least one of the impeller-housing-side second contact surface 24(24b) and the bearing-housing-side second contact surface 26(26 b).
According to the above configuration, in the rotary machine 10 in which the fastening member 22(22c) is a bolt configured to urge the bearing-housing-side second contact surface 26(26b) toward the impeller-housing-side second contact surface 24(24b), it is possible to suppress vibration and noise generated in the rotary machine 10.
Further, the recessed portion 32 is formed on both contact surfaces to which the pressing force is applied by the bolt 22(22c), whereby the vibration damping effect can be improved.
Further, since the recess 32 is formed by using the existing abutment surface existing in the existing fastening member 22(22c), the modification of the rotary machine is not required.
In some embodiments, as shown in fig. 8, a plurality of recesses 32(32a, 32b, 32c) are formed that are provided at intervals along the circumferential direction of the rotary shaft 12.
According to this configuration, the impact damping effect of the plurality of recesses 32 formed in the circumferential direction of the rotary shaft 12 can be further improved.
Fig. 12 shows an example in which the fastening member 22(22b) is a snap ring, and the concave portion 32(32a) is formed in the fastening member side second contact surface 28(28 b). Fig. 13 shows the result of the state where the snap ring 22(22b) was mounted on the automobile turbocharger as shown in fig. 10 and the radiation noise was measured. In fig. 13, a line X represents a case where the snap ring 22(22b) is used, and a line Y represents a case where a snap ring in which the surface of the snap ring 22(22b) is knocked to be flat is used as a comparative example.
As can be seen from this figure, when the snap ring 22(22b) indicated by the line X is used, the radiation noise is reduced as compared with the comparative example.
Fig. 14 shows a snap ring 22(22b) in which convex portions 33(33a) are formed at four locations of the fastening member side second contact surface 28(28b) of the snap ring 22(22b), and concave portions 32(32a) having flat surfaces are formed at the portions other than the convex portions 33(33 a). Fig. 15 shows the result of measuring the state of radiation noise when the snap ring 22(22b) is mounted on the automobile turbocharger as shown in fig. 10. In fig. 15, a line X indicates a case where the snap ring 22(22b) is used, and a line Y indicates a case where the snap ring 22(22b) having the fastening member side second contact surface 28(28b) as a flat surface is used as a comparative example.
As can be seen from this figure, when the snap ring 22(22b) indicated by the line X is used, the radiation noise is reduced as compared with the comparative example.
Industrial applicability
According to some embodiments, vibration and noise generated in a rotary machine can be suppressed with a simple structure.
Description of the symbols
10 rotating machine
12 rotating shaft
14(14a, 14b) impeller
14a compressor impeller
14b turbine wheel
16(16a, 16b) impeller housing
16a compressor housing
16b turbine housing
18 bearing shell
19 bearing
20(20a, 20b, 20c, 20d) fastening part
22(22a, 22a, 22c) fastening means
22a connection mechanism
22b snap ring
22c bolt
24(24a, 24b) impeller housing side abutment surfaces
24a impeller housing side first abutment surface
24b impeller housing side second abutment surface
26(26a, 26b) bearing housing side abutment surfaces
26a bearing housing side first abutting surface
26b bearing housing side second abutment surface
28(28a, 28b) fastening member side abutment surface
28a fastening member side first abutment surface
28b fastening member side second abutment surface
30(30a, 30b, 30c, 30d) thin plate member
32(32a, 32b, 32c, 32d) recess
33(33a, 33b) convex part
34 impeller housing side flange part
36 bearing housing side flange portion
38 impeller housing side projection
40 bearing housing side projection
41 annular groove
42 first annular portion
44 disc part
46 second annular portion
47 sealing element
48 bearing housing side extension
50 impeller housing side bolt receiving portion
52 impeller housing side extension
54 threaded hole
56 washer

Claims (12)

1. A rotary machine is provided with:
a rotating shaft;
an impeller attached to the rotating shaft;
an impeller housing that houses the impeller;
a bearing housing that houses a bearing that rotatably supports the rotating shaft and is fastened to the impeller housing;
a fastening member that fastens the impeller housing and the bearing housing in an axial direction of the rotary shaft,
the rotary machine is characterized in that,
the impeller case has an impeller case side abutting surface extending in a direction intersecting an axial direction of the rotary shaft at a fastening portion to which a fastening force is applied by the fastening member, the impeller case side abutting surface including an impeller case side first abutting surface abutting against the fastening member and an impeller case side second abutting surface abutting against the bearing case,
the bearing housing has a bearing housing side abutting surface extending in a direction intersecting with an axial direction of the rotary shaft at the fastening portion, the bearing housing side abutting surface includes a bearing housing side first abutting surface abutting against the fastening member and a bearing housing side second abutting surface abutting against the impeller housing,
the fastening member has a fastening member side abutment surface extending in a direction intersecting with an axial direction of the rotary shaft, the fastening member side abutment surface includes a fastening member side first abutment surface abutting the impeller housing and a fastening member side second abutment surface abutting the bearing housing,
a thin plate member that is configured separately from the impeller housing, the bearing housing, and the fastening member is provided at least one of between the impeller housing side first contact surface and the fastening member side first contact surface, between the bearing housing side first contact surface and the fastening member side second contact surface, and between the impeller housing side second contact surface and the bearing housing side second contact surface,
the impeller housing has an impeller housing side flange portion extending radially outward of the rotary shaft,
the bearing housing has a bearing housing side flange portion that abuts the impeller housing side flange portion, the bearing housing side flange portion extending radially outward of the rotary shaft,
the impeller housing side second abutting surface is formed on the impeller housing side flange portion, and the bearing housing side second abutting surface is formed on the bearing housing side flange portion,
the fastening member is a connecting mechanism for sandwiching the impeller housing side flange portion and the bearing housing side flange portion,
the thin plate member is a single thin plate member, and is positioned between the impeller housing side first abutting surface and the fastening member side first abutting surface, and between the bearing housing side first abutting surface and the fastening member side second abutting surface.
2. Rotating machine according to claim 1,
at least one of the impeller housing side first abutting surface, the impeller housing side second abutting surface, the bearing housing side first abutting surface, the bearing housing side second abutting surface, the fastening member side first abutting surface, and the fastening member side second abutting surface has at least one recess.
3. Rotating machine according to claim 2,
the at least one recess includes a plurality of recesses provided at intervals in a circumferential direction of the rotary shaft.
4. Rotating machine according to claim 2 or 3,
the at least one recess is formed in at least one of the two abutment surfaces constituting at least one of the positions between the impeller-housing-side first abutment surface and the fastening-member-side first abutment surface where the thin plate member is located, between the bearing-housing-side first abutment surface and the fastening-member-side second abutment surface, and between the impeller-housing-side second abutment surface and the bearing-housing-side second abutment surface.
5. A rotary machine is provided with:
a rotating shaft;
an impeller attached to the rotating shaft;
an impeller housing that houses the impeller;
a bearing housing that houses a bearing that rotatably supports the rotating shaft and is fastened to the impeller housing;
a fastening member that fastens the impeller housing and the bearing housing in an axial direction of the rotary shaft,
the rotary machine is characterized in that,
the impeller case has an impeller case side abutting surface extending in a direction intersecting an axial direction of the rotary shaft at a fastening portion to which a fastening force is applied by the fastening member, the impeller case side abutting surface including an impeller case side first abutting surface abutting against the fastening member and an impeller case side second abutting surface abutting against the bearing case,
the bearing housing has a bearing housing side abutting surface extending in a direction intersecting with an axial direction of the rotary shaft at the fastening portion, the bearing housing side abutting surface includes a bearing housing side first abutting surface abutting against the fastening member and a bearing housing side second abutting surface abutting against the impeller housing,
the fastening member has a fastening member side abutment surface extending in a direction intersecting with an axial direction of the rotary shaft, the fastening member side abutment surface includes a fastening member side first abutment surface abutting the impeller housing and a fastening member side second abutment surface abutting the bearing housing,
a thin plate member that is configured separately from the impeller housing, the bearing housing, and the fastening member is provided at least one of between the impeller housing side first contact surface and the fastening member side first contact surface, between the bearing housing side first contact surface and the fastening member side second contact surface, and between the impeller housing side second contact surface and the bearing housing side second contact surface,
the impeller housing has an impeller housing side projection extending radially inward of the rotary shaft,
the bearing housing has a bearing housing-side projection that abuts the impeller housing-side projection, the bearing housing-side projection extending radially outward of the rotary shaft,
the impeller-housing-side second abutment surface is formed on the impeller-housing-side protrusion, and the bearing-housing-side second abutment surface is formed on the bearing-housing-side protrusion,
the fastening member is a snap ring fitted into an annular groove formed in an inner peripheral surface of the impeller housing, and the outer peripheral portion of the snap ring is fitted into the annular groove to apply a force to the bearing housing side second contact surface toward the impeller housing side second contact surface.
6. Rotating machine according to claim 5,
the thin plate member is located between the impeller-housing-side second abutting surface and the bearing-housing-side second abutting surface.
7. Rotating machine according to claim 5,
the thin plate member is located between the fastening member-side second abutment surface and the bearing housing-side first abutment surface.
8. Rotating machine according to claim 6,
the thin plate member is integrally formed with a first annular portion, a disc portion, and a second annular portion,
the first annular portion is located between the top surface of the impeller-casing-side projection and the end surface of the bearing casing, and extends in the axial direction of the rotary shaft,
the disc portion is located between the impeller housing side second abutting surface and the bearing housing side second abutting surface, extends in a radial direction of the rotary shaft,
the second annular portion is located between a top surface of the bearing-housing-side protrusion and an end surface of the impeller housing.
9. A rotary machine is provided with:
a rotating shaft;
an impeller attached to the rotating shaft;
an impeller housing that houses the impeller;
a bearing housing that houses a bearing that rotatably supports the rotating shaft and is fastened to the impeller housing;
a fastening member that fastens the impeller housing and the bearing housing in an axial direction of the rotary shaft,
the rotary machine is characterized in that,
the impeller case has an impeller case side abutting surface extending in a direction intersecting an axial direction of the rotary shaft at a fastening portion to which a fastening force is applied by the fastening member, the impeller case side abutting surface including an impeller case side first abutting surface abutting against the fastening member and an impeller case side second abutting surface abutting against the bearing case,
the bearing housing has a bearing housing side abutting surface extending in a direction intersecting with an axial direction of the rotary shaft at the fastening portion, the bearing housing side abutting surface includes a bearing housing side first abutting surface abutting against the fastening member and a bearing housing side second abutting surface abutting against the impeller housing,
the fastening member has a fastening member side abutment surface extending in a direction intersecting with an axial direction of the rotary shaft, the fastening member side abutment surface includes a fastening member side first abutment surface abutting the impeller housing and a fastening member side second abutment surface abutting the bearing housing,
at least one of the impeller-housing-side first abutting surface, the impeller-housing-side second abutting surface, the bearing-housing-side first abutting surface, the bearing-housing-side second abutting surface, the fastening-member-side first abutting surface, and the fastening-member-side second abutting surface has at least one recess, and,
the at least one recess includes a plurality of recesses provided at intervals in a circumferential direction of the rotary shaft,
the plurality of concave portions satisfy any one of the following conditions (a) to (c):
(a) a plurality of the concave portions are formed by a plurality of concave portions having flat surfaces at equal intervals in a circumferential direction of the rotary shaft, and convex portions having flat surfaces are formed between the concave portions;
(b) a plurality of concave portions formed at equal intervals between adjacent convex portions formed in a wave-shaped cross section;
(c) the plurality of concave portions are formed at equal intervals between arcs in a cross section formed at equal intervals.
10. Rotating machine according to claim 9,
the bearing housing has a bearing housing side extension extending radially outward of the rotary shaft,
the impeller housing has an impeller housing-side bolt receiving portion located further to the radially outer side of the rotary shaft than the bearing housing-side extension portion, and an impeller housing-side extension portion abutting against the bearing housing-side extension portion and extending from the impeller housing-side bolt receiving portion to the radially inner side of the rotary shaft,
the impeller-housing-side second abutment surface is formed on the impeller-housing-side extension, and the bearing-housing-side second abutment surface is formed on the bearing-housing-side extension,
the fastening member is a bolt screwed into a screw hole formed in the impeller housing-side bolt receiving portion, and biases the bearing housing-side second contact surface toward the impeller housing-side second contact surface by being screwed into the screw hole.
11. A rotary machine is provided with:
a rotating shaft;
an impeller attached to the rotating shaft;
an impeller housing that houses the impeller;
a bearing housing that houses a bearing that rotatably supports the rotating shaft and is fastened to the impeller housing;
a fastening member that fastens the impeller housing and the bearing housing in an axial direction of the rotary shaft,
the rotary machine is characterized in that,
the impeller case has an impeller case side abutting surface extending in a direction intersecting an axial direction of the rotary shaft at a fastening portion to which a fastening force is applied by the fastening member, the impeller case side abutting surface including an impeller case side first abutting surface abutting against the fastening member and an impeller case side second abutting surface abutting against the bearing case,
the bearing housing has a bearing housing side abutting surface extending in a direction intersecting with an axial direction of the rotary shaft at the fastening portion, the bearing housing side abutting surface includes a bearing housing side first abutting surface abutting against the fastening member and a bearing housing side second abutting surface abutting against the impeller housing,
the fastening member has a fastening member side abutment surface extending in a direction intersecting with an axial direction of the rotary shaft, the fastening member side abutment surface includes a fastening member side first abutment surface abutting the impeller housing and a fastening member side second abutment surface abutting the bearing housing,
at least one of the impeller-housing-side first abutting surface, the impeller-housing-side second abutting surface, the bearing-housing-side first abutting surface, the bearing-housing-side second abutting surface, the fastening-member-side first abutting surface, and the fastening-member-side second abutting surface has at least one recess,
the impeller housing has an impeller housing side projection extending radially inward of the rotary shaft,
the bearing housing has a bearing housing-side projection that abuts the impeller housing-side projection, the bearing housing-side projection extending radially outward of the rotary shaft,
the impeller-housing-side second abutment surface is formed on the impeller-housing-side protrusion, and the bearing-housing-side second abutment surface is formed on the bearing-housing-side protrusion,
the fastening member is a snap ring fitted into an annular groove formed in an inner peripheral surface of the impeller housing, and the outer peripheral portion of the snap ring is fitted into the annular groove to apply a force to the bearing housing side second contact surface toward the impeller housing side second contact surface.
12. Rotating machine according to claim 11,
the recess is formed in the fastening member-side second abutment surface.
CN201680084109.5A 2016-03-30 2016-03-30 Rotary machine Active CN109219693B (en)

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JP6606599B2 (en) 2019-11-13
US20190101023A1 (en) 2019-04-04
EP3418530B1 (en) 2020-11-11
US10934887B2 (en) 2021-03-02
CN109219693A (en) 2019-01-15
EP3418530A4 (en) 2019-08-21
EP3418530A1 (en) 2018-12-26
WO2017168634A1 (en) 2017-10-05

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